Multi-chambered pump

ABSTRACT

A multi-chambered self-priming rotary pump having a pair of eccentric cams, each in contact with opposite sides of a rotor plate at one point and positioned 180° out of phase so that the convex side of one cam is in direct opposition to a concave side of the other cam. At one point of contact on the convex curves, the cams bear against the side surfaces of the rotor which in turn forms a running seal with the bore of a housing to define two symmetrical enclosures at each side of the rotor. During rotation, a split core closure valve reciprocates between the surfaces of the cams and in so doing, the closure valve functions to produce an area of compression to the front of its travel with an area of vacuum to the rear of its travel. As one chamber phases out of cycle, its counterpart is producing maximum outputs. During rotation, a rotor impeller duct functions to pressure load the closure valve and provide impetus to the injection (clockwise rotation) or ejection (counterclockwise rotation) of pump fluids. The impeller duct is in communication with an annular housing duct which communicates with a housing fitting orifice. Completing the fluids cycle are shaft ports in communication with a ducted shaft which in turn communicates with a cam fitting orifice.

BRIEF DESCRIPTION OF THE INVENTION

The present invention relates to a multi-chambered pump of constantvolume principle, but designed to incorporate centrifugal thrust in thedelivery system. According to the invention, a self primingmulti-chambered pump is provided for pumping fluids in either direction.A pump shaft drives an integral rotor plate between two eccentric cams.The cams are positioned 180° out of phase so that the convex side of thefirst cam is in direct opposition to the concave side of the other cam.Each cam bears against an opposite surface of the rotor plate at onearea which in turn forms a running seal with a bore of the housing todefine two symmetrical enclosures at each side of the rotor.

During rotation, a fluid pressurized closure valve reciprocates on theslightly convex and concave surfaces of the cams. In so doing, theclosure valve functions to produce an area of compression to the frontof its travel and a vacuum to the rear of its travel. As one chamberphases out of the intake exhaust cycle, its counterpart is in theprocess of producing maximum outputs.

The multi-chambered pump utilizes rotational forces to add impetus tothe movement of fluids through the pump and to pressurize the closurevalve seal at the cam surfaces. Assuming clockwise rotation, fluidrouting follows a path from a housing fitting orifice to an annularhousing groove. An off-center impeller duct milled in the concentricsurface of the rotor plate rotatably picks up fluids from the annularhousing duct and transfers them through the split half closure valvethereby activating pressure on the bearing surfaces of that valve.Finally, at the back of the valve, fluids forcibly inject the vacuumchambers of the pump. Forward of the closure valve, the compressionchambers force fluids through shaft ports to a shaft core duct which inturn communicates with a cam block fitting orifice to permit the exit ofexhaust fluids.

During counterclockwise rotation, the flow cycle is reversed and theimpeller duct functions to centrifugally eject fluids from thecompression chambers. Spiral grooves on the perimeter of the rotor plateprovide additional compression seal. An integral system of shaft valvingprevents pressure blow-by from compression to intake chambers. Shaftports are located adjacent to the sides of the rotor so that the pitchconfiguration of the cams can function to open and close the portsduring shaft rotation.

An object of the present invention, the multi-chambered pump, is toincrease the priming and filling potential of constant volume pumps byimpeller injecting the vacuum chambers.

Another object of the invention is to increase the delivery momentum andpressures of constant volume pumps through centrifugal evacuation of thecompression chambers.

A further object of the invention is to provide fluid pressurization ofthe closure valve to improve the cam bearing seal of that valve, and tocompensate for closure valve wear.

An additional object of the invention is the provision of an axial portvalving system to reduce working parts and manufacturing costs.

Pump design features will be more easily understood when considered inconnection with the following detailed description in which likereference numerals designate like parts throughout the Figures thereofand wherein:

FIG. 1 is a perspective view, partially sectioned, of the preferredembodiment of the present invention;

FIG. 2 is a front view of the rotor shaft and ducted core of theembodiment of FIG. 1 as seen from line 2 of FIG. 1;

FIG. 3 is an exploded view of part 18, a three piece closure valuve;

FIG. 4 is a cross sectional view taken along lines 4--4 of FIG. 1;

FIG. 5 is a cross sectional view taken along lines 5--5 of FIG. 1;

FIG. 6 is a partially sectioned front view taken along line 2 of FIG. 1;

FIG. 7 is a sectioned view similar to FIG. 6 with a housing rotatedcounterclockwise 90°.

DETAILED DESCRIPTION OF THE DRAWING

Referring to FIG. 1, a bored housing 11 carries rotatable shaft 12 withcore duct 13 and integral rotor plate 14. Rotor plate 14 carriesimpeller duct 15 and rotor channel 16. Sector slot 17 of rotor plate 14carries a reciprocating closure valve 18. Closure valve 18 bears againsteccentric surface 19 of cam block 20 and on the other side against thesurface (not shown) of eccentric cam block 21. The contacting ofeccentric cams 20 and 21 are geometrically formed so that the peripheryof the eccentric face of each cam defines an elliptical plane and theedge of the axial bore in each cam defines an ellipitical plane. Anyradial line between the two ellipses is at 90° to the axis of the pump.Retainer plate 22 resides between shaft shoulder 23 and retainer clip 24to limit shaft end play. Packing gland 25 forms a seal with cam block 21and shaft 12. O-rings 39 and 40 seal cam blocks 20 and 21 with housing11.

A housing fitting orifice 26 communicates with annular housing duct 27which is turn communicates with rotor impeller duct 15. Impeller duct 15vents through duct 28 of closure valve 18 to communicate with rotorchannel 16 which exits to both side of rotor plate 14. Shaft port 29 andshaft port 30 (not shown) communicate with rotor duct 13 which exhauststhrough cam fitting orifice 31 of cam block 20. Compression chamber 32is shown ahead of closure valve 18 between rotor plane 14 and eccentriccam 21. Intake chamber 35 is shown behind closure valve 18 between rotorplate 14 and eccentric cam 20. Machine screw 36 passes through clearancehole 37 in retainer plate 22, cam block 21 and housing block 11 tothread into cam block 20. Four such screws assemble the pump.

Referring to FIG. 2, rotatable shaft 12 is shown carrying integral rotorplate 14 and retainer ring 24. Sector slot 17 has been machined atradial lines to the rotor axis to form a wedge shaped void in rotor 14.Rotor plate 14 displays impeller duct 15 bored to communicate with rotorchannel 16. Channel 16 is semicircular and ducts to both sides of rotorplate 14. Shaft ports 29 and 30 communicate with core duct 13. Spiralgroove 38 is shown as a helical recess on the perimeter of rotor plate14.

Referring to FIG. 3, closure valve 18 shows split core 18B sandwichedbetween support plates 18A and 18C. Slotted duct 28 penetrates 18A, 18Band 18C.

Referring to FIG. 4, sectioned housing 11 rotatable carries shaft rotorplate 14 and closure valve 18. Housing fitting orifice 26 communicateswith annular housing duct 27 which in turn communicates with impellerduct 15. Impeller duct 15 vents through closure valve duct 28 tocommunicate with rotor channel 16.

Referring to FIG. 5, bored housing 11 rotatably carries rotor plate 14and closure valve 18. Rotor channel 16 is shown venting behind closurevalve 18, and exhaust port 29 is shown in communication with duct 13 ofrotor shaft 12. Cam block 21 is shown sectioned near the point at whichit forms a running seal with rotor plate 14.

Referring to FIG. 6 and FIG. 7, housing 11 rotatable carries plate 14which in turn carries closure valve 18. Closure valve 18 is in contactwith the eccentric surfaces of cams 20 and 21. O-rings 39 and 40together with packing gland 25 seal the unit. Annular housing duct 27communicates with impeller duct 15 which vents through closure valveduct 28 to communicate with rotor channel 16. Rotor channel 16communicates with intake chambers 34 and 35 at the rotor sides.

In FIG. 6, the eccentric face of cam block 21 and rotor plate 14 formcompression chamber 32 separated from intake chamber 34 by closure valve18. The eccentric face of cam block 20 and rotor plate 14 formcompression chamber 33 which is separated from intake chamber 35 byclosure valve 18.

In FIG. 7, the eccentric face of cam block 21 and rotor plate 14 formcompression chamber 32 which is separated from intake chamber 34 byclosure valve 18. The seal surface of cam block 20 bears at dead centeragainst closure valve 18 to form a single continuous chamber 35 withrotor plate 14.

OPERATION

Assuming a clockwise rotation of pump shaft 12, fluids enter the pumphousing at fitting orifice 26 which communicates with annular housingduct 27. During rotation of rotor plate 14, the fluids from duct 27 arerotatably forced into impeller duct 15 as shown in FIG. 4. The fluidsthen pass through a slotted duct 28 of closure valve 18. Pressure fromthe fluids act to spread split piece 18B of the closure valve shown inFIG. 3 thereby improving the chamber seal and compensating for closurevalve wear. From duct 28, the fluids enter rotor channel 16, visible inFIG. 4 as a semicircle. Rotor channel 16 fills intake chambers 34 and 35located to either side of the rotor plate as indicated in FIG. 6. Inthis manner, the vacuum chambers of the pump are rotationally chargedwith fluids. Spiral groove 38 as shown in FIG. 2 moves in a helicalmanner around the surface of the rotor during rotation to function as acompression seal.

Compression and intake chambers of the pump are formed as thereciprocating closure valve functions to limit chamber displacements atboth sides of the rotor. In FIG. 7, housing 11 has been rotatedcounterclockwise 90° from FIG. 6 to demonstrate the effect of shaftrotation on chamber functions and closure valve position. In FIG. 6,intake chambers 34 and 35 are filling. Simultaneously, compressionchambers 32 and 33 at the front of the closure valve are emptying theircontents into core duct 13 through shaft ports 29 and 30. Duct 30 isshown in communication with cam fitting orifice 31 which exits thehousing. As further rotation diminishes the distance between the closurevalve seal and the cam bearing surface, fluids will continue to exitboth shaft ports until, as in FIG. 7, one of the chambers is fullyemptied. In FIG. 7, chamber 33 no longer exists as such since theclosure valve is now positioned at dead center against the rotor bearingsurface of cam 20. It is also evident in FIG. 7 that the closure valvehas moved fully to the right, following the pitch line of the cams, andthat the bored axial surface of cam block 20 now functions to blockshaft port 30 to prevent blowby of compressed fluids. Cam block 20 hascompleted its cycle and cam block 21 is at maximum output.

It is understood that rotation of shaft 12 in a counterclockwisemovement results in a reversal of the flow cycle and changes thefunction of the rotor impeller duct. The impeller duct incounterclockwise rotation functions to centrifugally evacuate thecompression chambers whereas the intake chambers revert to vacuum fillprinciples. Obviously, pump requirements dictate the direction of pumprotation. When priming requirements are of foremost importance, thevacuum chambers wil be impeller filled in clockwise rotation. Whereexhaust impetus is required, centrifugal force will be used to helpevacuate the exhaust chambers in counterclockwise rotation.

The multi-chambered pump described in this disclosure incorporates inits design but makes no inventive claim for the following designspecifications;

A bored housing block having first and second eccentric cam blocksdisposed at each end thereof;

A rotor rotatably mounted within said housing block and said eccentriccams, said rotor comprising a ducted core and a rotor plate, said rotorplate having first and second sides;

Said first and second eccentric cams being in contact with first andsecond opposite sides of said rotor plate, respectively, at contactareas 180° removed from each other;

A closure valve carried by said rotor plate and disposed between firstand second inside surfaces of said first and second eccentric cams,respectively, and forming a seal therewith;

A cylindrical rotor shaft having bored ports at one side of said closurevalve and immediately adjacent to either side of said rotor plate, saidports coupled with a core duct of the rotor shaft and with thedisplacement chambers of the pump, said shaft ports in axial contactwith the pitch line configerations of a first and second cam block toeffect opening and closing of shaft ports.

The foregoing disclosure relates to only a preferred embodiment of theinvention, and is not intended to cover all changes and modifications ofthe example of the invention herein chosen, for the purposes of thedisclosure, which do not represent departures from the spirit and scopeof the invention.

The invention claimed is:
 1. A multi-chambered self priming pumpcomprising:a bored housing block having first and second eccentric camsdisposed on each end thereof, said first and second eccentric cams eachhaving a bore therethrough. a rotor plate rotably mounted within saidhousing block on a rotor shaft that passes through the bores of saidfirst and second eccentric cams, said rotor plate being disposed betweensaid first and second eccentric cams and said rotor plate having firstand second lateral sides and a ducted core, said first and secondeccentric cams and being in contact with said first and second lateralsides of said rotor plate, respectively, at contact areas 180° removedfrom each other, closure valve means carried by said rotor plate andbeing disposed between inside surfaces of said first and secondeccentric cams and forming a rotating seal therewith, said rotor platehaving a channel passing through its width at a point eccentricallylocated from the axis of said shaft, and said rotor plate havingimpeller duct means directed inwardly from its outer surface in themanner of a chord along a path offset from the axis of said rotor plateand connected with said rotor plate channel 16 intermediate its ends,said channel extending from said first lateral side of said rotor plateto said second lateral side, said channel only being open at itsopposite ends with the exception of the opening formed where theimpeller duct means intersects said channel, said impeller duct meansopening in the direction of rotor rotation functioning to produce directfrontal injection of fluid into the pumps intake chambers when saidrotor plate is rotated.
 2. A multi-chambered, self priming pump asrecited in claim 1 further comprising a pair of spiral grooves on theouter peripheral surface of said rotor plate that wind helicallyinwardly and function as a compression seal.
 3. A multi-chambered, selfpriming pump as recited in claim 1 further comprising a pair of shaftports on opposite sides of said rotor plate that are in communicationwith the core duct of said shaft, said cam members being oriented withsaid shaft ports such that as said shaft is rotated, the cam members actupon interface with said shaft ports as a valve for the chamber formedbetween the rotor plate, the shaft, the cam member, and the bore of saidhousing block.
 4. A multi-chambered, self priming pump as recited inclaim 1 wherein said impeller duct vents through a duct of said closurevalve means to communicate with said rotor plate channel.
 5. Amulti-chambered, self priming pump as recited in claim 4 wherein saidclosure valve means comprises a plurality of wedge-shaped members, eachof said wedge-shaped members having planar operating surfaces with aradial orientation to the axis of said rotor and one of saidwedge-shaped members being split whereby pressure from fluid passingthrough the closure valve means acts to spread the split pieces therebyimproving the chamber seal and also compensating for closure valve wear.6. A multi-chambered self priming pump as recited in claim 5 whereinsaid rotor plate and shaft have a wedge shaped sector slot into whichclosure valve means is positioned, said slot being wider axially thenthe width of said wedge-shaped members to allow for their reciprocatingtravel as the shaft is rotated.
 7. A multi-chambered, self priming pumpas recited in claim 6 wherein said slot is also sufficiently deepaxially to allow said wedge-shaped members to travel radially outwardlyto compensate for wear along the peripheral surface of said wedge-shapedmembers.